Instinctive wringer

ABSTRACT

A motion translating and force transmitting device especially as applied to an instinctive wringer includes a rocker arm having wing members thereon which translate pivoting motion of the rocker arm about an axis to either end of a bell crank which is pivoted about an axis parallel to the plane of motion of the rocker arm. Cam means are indexed against a spring loaded index pin and are de-indexed by the reaction of the cam face with a cam shifting pin outwardly from the cam pivot of the operative index. A component of the force of the planar pivoting motion of the rocker arm is transmitted to either end of the bell crank so that, while the bell crank pivots, the moment-arm of the force being transmitted about the bell crank pivot remains constant.

United States Patent Taylor 5] Mar. M, 11972 [54] INSTINCTIVE WRINGER [72] Inventor: Ronald W. Taylor, Guelph, Ontario,

Canada [73] Assignee: GSW Limited-GSW Limitee, Toronto, On-

tario, Canada [22] Filed: June 29, 1970 i211 Appl. No.: 50,413

[52] US. Cl. ..68/253 A, 68/255, 68/269 CA [51] lnt.Cl.

[58] Field of Search ..68/255, 269 CA, 253 A; 74/269 [56] References Cited UNITED STATES PATENTS 2,937,517 5/1960 Hughes ..68/255 2,883,865 4/1959 Lyman..... ....74/569 3 ,494, l 55 2/1970 Horrobin ..68/255 Primary Examiner-Leon G. Machlin Attorney-Douglas S. Johnson ABSTRACT A motion translating and force transmitting device especially as applied to an instinctive wringer includes a rocker arm having wing members thereon which translate pivoting motion of the rocker am about an axis to either end of a bell crank which is pivoted about an axis parallel to the plane of motion of the rocker arm. Cam means are indexed against a spring loaded index pin and are de-indexed by the reaction of the cam face with a cam shifting pin outwardly from the cam pivot of the operative index. A component of the force of the planar pivoting motion of the rocker arm is transmitted to either end of the bell crank so that, while the bell crank pivots, the moment-arm of the force being transmitted about the bell crank pivot remains constant.

5 Claims, 9 Drawing Figures Patented March 14, 1972 3 Sheets-Sheet 1 t 72 V E I l *5 Iii 1 60 H V 2%; 54 9O 77 I iii? 68 70 l 79 86 a! 72 1 2 r 84 IN'VENIOR.

RONALD W. TAYLOR Attorney Patented March $4, 1972 v 3,648,489

3 Sheets-Sheet 2 INVENTOR. RONALD W. TAYLOR Attorney Patented Mam 14 3 SheetsSheet 3 INVENTOR. RONALD w. TAYLOR BY M Attorney INSTINCTIVE WRINGIER BACKGROUND OF THE INVENTION This invention relates to a motion translating means, particularly one which is adapted to translate pivoting motion of a first body in a first plane into linear motion of another body or a part of another body in a direction perpendicular to that plane. The invention is particularly illustrated and discussed with respect to instinctive wringers, and teaches a clutch shifting means for instinctive wringers whereby the drive mechanism which drives at least one of the rollers in a wringer is stopped upon pivoting motion of the wringer about an axis, usually the axis of the drive shaft from which the power driving the driven roller is derived.

An instinctive wringer is a wringer which has a safety fea ture such that an instinctive reaction of the operator, say when material being passed through the wringer starts to wrap around one of the rollers thereof or when a part of the body of the operator or another person is drawn or enters between the rollers-such an instinctive reaction being manifested by a pull away from the rollers of the material or part of the body therebetween-causes or tends to cause a pivoting motion of the rollers about the axis of the drive shaft from which the power driving at least one of the rollers is derived, with the result that the transfer of driving power to the driven roller is terminated. In an instinctive wringer of the type specifically illustrated and referred to in this application, the pressure between the rollers is not released at the same time as the drive to the rollers is stopped, although additional apparatus outside the scope of this application can be provided to do so. In any event, a release bar or button is provided in any wringer by which the pressure between the rollers thereof may be released simply by striking the same.

The most notable prior art relating to instinctive wringers includes Canadian Pat. Nos. 480,898 to 480,903 inclusive, all issued Feb. 5, 1952 to Walter Lee Kauffman II (especially Pat. Nos. 480,899; 480,901 and 480,903); and also Canadian Pat. No. 523,043, issued Mar. 20, 1956 to William B. Geuscher. However, none of the prior art particularly teaches a motion translating means which includes force transmitting means such that the force being transmitted thereby-which force is related to and is the result of pivoting motion of the wringeris transmitted to the mechanism which stops driving action of the driven roller (roll-stop operation) through a substantially constant moment-arm. Further, the lack of the constant moment-arm force transmitting means in any motion translating means which may have previously been installed on instinctive wringers has resulted in an instinctive wringer having an unsymmetrical operation, i.e., much greater pull in one direction than in the other has been required to initiate pivoting motion of the wringer and thereby to initiate roll-stop operation thereof, and in some cases such a pull could only be in one direction or the other depending upon the direction in which the rollers were driving. Certain of the prior art wringers, particularly as taught in the Kauffman Pat. Nos. 480,899 and 480,903, have relied upon a delicate balance of spring forces in order to keep the wringer in an operating condition with drive applied to the rollers, and for release of the drive so as to stop the rollers.

SUMMARY OF THE INVENTION It is a purpose of this invention to provide a motion translating means which is adapted to translate pivoting motion of a rigid body moving in a plane into linear motion of at least a part of another body in a direction substantially perpendicular to said plane, and where the force transmitted from the first of said bodies to the second is translated through a substantially constant moment-arm.

A further object of this invention is to provide an instinctive wringer having clutch shifting means adapted to stop the transmission of driving power to a driven roller in said wringer upon pivoting motion of the roller in a plane substantially perpendicular to and about the axis of a drive shaft, irrespective of the direction of pivoting motion or the direction in which the roller is being driven.

A still further object of this invention is to provide an instinctive wringer having symmetrical and consistent roll-stop operation and utilizing essentially solid, incompressible integers; and which operates without reliance upon a balance of spring forces within the instinctive wringer.

Yet another object of this invention is to provide an instinctive wringer which is adjustable so as to minimize the time delay from initiation of the instinctive, pivoting motion of the rollers until the transmission of driving power is terminated. This feature therefore provides an instinctive wringer which may be easily adjusted in the field by qualified service personnel, and at the same time the feature provides an instinctive wringer in which factory or. field adjustments can be made to accommodate the minor variations which may happen with respect to dimensional tolerances of mass produced, manufactured items which may be integers and parts of the instinctive wringer.

BRIEF DESCRIPTION OF THE DRAWING These and other objects and features of the invention are explained and will become obvious in the following description, taken in association with the drawings, in which:

FIG. 1 is a perspective, partially exploded view of a wringer and wringer head embodying the present invention;

FIG. 2 is a perspective, partially diagrammatic view of the drive mechanism and a portion of the roll-stop mechanism of the instinctive wringer according to this invention;

FIG. 3 shows certain of the integers of FIG. 2 in driving position opposite to that as illustrated in FIG. 2;

FIG. 4 is a perspective, partially cutaway and partially exploded view of the housing for the drive mechanism and of the rocker arm mounted in pivotable relationship thereon; F IGS.

FIG. 5 is an exploded view showing the adjustable relationship of certain of the lower bearing integers of the rocker arm in FIG. 4;

FIGS. 6, 7 and 8 are diagrammatic views showing the relationship of certain of the integers of the roll-stop mechanism in the various relative positions as illustrated therefor in FIG. 1, 2 and 3 respectively; and

FIG. 9 is a diagrammatic view showing the relationship of the force transmitting means through the motion translating means according to this invention.

DESCRIPTION OF THE PREFERRED EMBODIMENT The wringer 10 of FIG. 1 includes a pair of rollers 12 and 14, a top frame 16, pressure release bar 18, drainboard 20, and a wringer head designated generally at 22. The wringer head includes a control handle 24, a rigid housing 26, an index plate 28 and a stem 30 through which the drive shaft shown at 32 in FIGS. 2 and 3 extends. A plurality of apertures 34 is formed around the periphery of the index plate 28, and lock means 36 is secured to the rigid housing 26 and conveniently includes a pin which is spring urged downwardly so that the entire wringer assembly may be swung about the post 30 when the lock means 36 is manually overcome. A cover plate 38 is secured by bolts 39 over the housing 26, thereby providing access to the drive mechanism of the wringer head 22. When the drive mechanism is in its operative position, it transmits driving force, in a manner to be discussed hereafter, to roller 14; and operative position of the drive mechanism is determined and may be manually set by turning the control handle 24 onequarter turn clockwise or counterclockwise when viewed from the end of the wringer assembly, thereby determining the direction in which the driven roller 14 and the other roller 12 will turn. A rocker arm designated generally at 40 is pivotably mounted to the rigid housing 26, as discussed hereafter.

The drive mechanism includes a drive shaft 32 having a key 42 at the bottom thereof to pick up driving power from another drive shaft installed within the post 30; thereby providing for the complete removal of the entire wringer assembly from the laundry apparatus on which it is installed for purposes of inspection, repair or replacement as may be necessary. In any event, the drive mechanism further includes an upper pinion 44 and a lower pinion 46 which are coaxial with the drive shaft 32, and which are rotatable thereon independently of the direction of rotation of the drive shaft; and a clutch 48 which is keyed to the drive shaft 32 by means of splines 50 formed on the drive shaft and corresponding splines formed axially within the clutch 48. A crown gear 52 meshes with the upper and lower pinions 44 and 46, and drives a shaft 54 which in turn may be keyed to a drive bearing 56-such as that illustrated in FIG. 4-from which the driving power for the roller 14 is ultimately derived. An upper bearing post 58, which may be an extension of the upper end of the drive shaft 32, is formed so that lateral support for the drive shaft by way of a bearing installed within the rigid housing 26 at the upper side thereof may be achieved.

A bearing block 60 is mounted on a pin 62 (as indicated in FIGS. 6 and 7), and the pin in turn is mounted in a pin block 64 which is secured to the inside planar face of a cam plate 66. The cam plate 66 is, in turn, keyed or otherwise secured to a shaft 68 to which the control handle 24-which is diagrammatically indicated at 70 in FIGS. 2 and 3-is secured. The shaft 68 is held within a bearing 70 on the rigid housing 26 so as to provide a fixed pivotbeing the axis of shaft 68for the cam plate 66. It will be noted that the pin 62 in pin block 64 is therefore eccentric with respect to the pivot of the cam plate 66.

Means are provided on the upper and lower ends of the clutch 48 to engage with the upper and lower pinions 44 and 46 respectively, and to disengage therefrom as required and as discussed in greater detail hereafter. Those means are conveniently two pairs of dogs 73 and 75 on the upper and lower ends of the clutch 48, one of each of the pairs of dogs 73 and 75 being shown respectively in FIGS. 2 and 3. Cavities are, of course, formed within the pinions for engagement with the dogs, such as those cavities shown at 79 in the lower pinion 46 in FIG. 3. The angles of the gear faces of dogs 73 and 75 and of the cavities 79 are chosen so as to assure positive driving engagement of the pinions to their respective cavities, and as well to assure disengagement from the cavities in either pinion upon a de-indexing operation, as discussed hereafter.

The direction of drive of the shaft 54, and thereby the roller 14, is determined by the engagement of the clutch 48 with either of the upper or lower pinions 44 and 46 respectively. Thus, with the control handle 24 turned 90 counterclockwise as in FIG. 2, the clutch 48 is engaged with the lower pinion 46. Because the direction of rotation of the drive shaft 32 is constant at all times (and indeed, the drive shaft 32 is rotating at all times that power is transmitted to it from within the post 30), the direction of rotation of the clutch 48 which is splined to the drive shaft is also constant. When the clutch 48 engages with the lower pinion 46 as in FIG. 2, the crown gear 52 and the shaft 54 are driven in clockwise direction, and so is roller 14. Because the crown gear 52 meshes with the upper pinion 44 at all times, it will be noted in FIG. 2 that the upper pinion is rotating in a direction counter to the direction of rotation of the drive shaft 32 together with the clutch 48 and lower pinion 46.

Likewise, when the clutch 48 is engaged with upper pinion 44 as illustrated in FIG. 3, the upper pinion 44 is driven in the same direction as the direction of rotation of the drive shaft 32, and the crown gear 52 and shaft 54 are driven in a counterclockwise direction as shown in FIG. 3. Also, in the same manner as explained above, the lower pinion 46 is driven in a direction counter to the direction of rotation of the drive shaft 32.

The instinctive safety feature of the wringer 10 as discussed generally above can be considered, with regard to FIG. 1, in the following manner. Suppose roller 14 is being driven; that is, control handle 24 is placed in either of its controlling positions so that the clutch 48 engages with either of the pinions 44 or 46 as discussed above. (The means whereby the driving condition of the roller 14 is maintained is discussed hereafter.)

' If a pull is made on the wringer anywhere beyond the wringer head 22 such that the rollers 12 and 14 and the top frame 16-- together with rocker arm 40 as discussed in greater detail hereafter-begin a pivoting motion about the axis of the drive shaft 32 and the pinions and clutch which are coaxial therewith, the clutch will be driven out of engagement with the pinion with which it was previously engaged by means to be discussed in greater detail hereafter, and the roller 14, together with the roller 12, will stop driving. That is to say, a pull away from the interface between rollers 12 and 14, such as by pulling on a material or other article which may be between the rollers 12 and 14, will stop drive to the rollers. Thus, imminent danger to a person or an article which might pass between the rollers 12 and 14 is substantially precluded by the ability to stop the driving power from being applied to the driven roller merely by the instinctive reaction of an operator or other person pulling back away from the rollers 12 and 14, irrespective of the direction in which the rollers may be driving, and irrespective of the direction of the pull. Of course, this capability is possible only when the force of the pull can be resolved so that at least a component thereof acts in a direction so as to tend to cause pivoting motion of the rollers about the axis of the drive shaft 32. Because the wringer assembly 10 is such that the wringer portion is pivotally but otherwise substantially rigidly mounted both with respect to the index plate 28 and post 30, and the rigid housing 26, any pivoting movement of the wringer assembly--especially as it may be manifested by a pivoting motion of the rollers 12 and 14 about the axis of drive shaft 32is in a plane which is substantially perpendicular to that axis.

The clutch 48 is maintained in driving relationship with either of pinions 44 or 46 by the secure indexing of the cam plate 66 against an index pin 72, in a manner discussed in greater detail hereafter. However, as noted above, the cam plate 66 carries the bearing block 60 which in turn rides in an associated groove 77 formed in the outer periphery of the clutch 48, and the indexing of the cam plate 66 in the position as shown in either of FIGS. 2 or 3 (or FIGS. 7 or 8) assures the driving relationship between the clutch 48 and either of pinions 46 or 44 respectively. It will be noted that the index pin 72 is urged upwardly by means of a coil spring 76 which is placed over the lower end thereof, and which is secured between a C-washer 78 and a footing 80 on the lower shoulder 82 which forms part of the rigid housing 26. Cam shifting pins 84 and 86 are supported at their bottom ends on a surface 88 (as indicated in FIGS. 2, 7 and 9), which surface is formed as a portion of a shift pin bell crank 90. The bell crank 90 is adapted to pivot about pivot pins 92 on an axis 94 thereof as indicated in FIG. 2; and the pivot pins 92 project outwardly from and are rigidly associated with the housing 26.

The bell crank 90 is generally U-shaped, and is mounted for pivoting movement about the pins 92. The net result of the pivoting movement of the bell crank 90 about pins 92 is manifested in an essentially up and down movement of the end of the bell crank most closely associated with the index pin 72 and the cam shifting pins 84 and 86; i.e., at surface 88 thereof. There is formed at each pivot end of the bell crank 90 a cutout 96 which effectively underlies the hole 98 formed therein to fit over the pin 92 on each side of the housing 26. Below the cutout 96 on each side of the shift pin bell crank 90, and therefore at each end of the legs of the U formed by the bell crank around the housing 26, there is a lobe 100. The lobe 100 acts as a force transmitting means to transmit force to the bell crank 90 at a constant moment-arm about the axis 94 of pivot pins 92, in a manner to be discussed hereafter.

FIG. 5 shows the manner in which a harness 102 wraps around the housing 26. The harness is secured by means of a bolt 104 through a slot 106 to the lower end 108 of the rocker arm 40, and the bolts 104 at each side of the rocker arm threadably engage the same in threaded, bolt-receiving recesses 110 formed thereon. The slot 106 is formed in the harness 102 so as to provide adjustment of the harness, as

discussed hereafter. A wing 112 is adapted to fit between the outer surface of the harness 102 and the inner surface of the head of bolt 104, with an inturned tab 114 extending into a recess 116 formed in the lower end 108 of rocker arm 40. The wing is out-turned at 118 so that a face 120 is formed thereon, which opposes each of the lobes 100 formed on the bell crank 90. The plane of each of faces 120 on wings 112 is essentially parallel to the axis 94 of pins 92 on the rigid housing 26.

It will now be seen that the wringer 10, and especially rollers 12 and 14 and the associated frame work, all of which is supported by the rocker arm 40, is pivotable about an axis which is defined by the axis of the drive shaft 32. Bearings are formed in the rocker arm at 122 over the upper bearing post 58, and at faces 124 and 126 of the housing 26 when associated with a pair of inturned bearing plates 128 formed in the lower end 108 of the rocker arm 40. In other words, rocker arm 40-and the associated rigid frame work within which the rollers 12 and 14 of wringer are maintained-is mounted for pivotable motion in a plane which is substantially perpendicular to the axis of the drive shaft 32, which is also the axis of the rigid body 26 housing the drive mechanism; and limited but independent pivotal relationship therefore exists between the rigid housing 26 and the rocker arm 40 mounted thereon. It is this relationship which allows the instinctive feature of the wringer to be operative because means are provided on the rocker arm 40 and the rigid housing 26 to sense pivoting motion of the one with respect to the other, and to translate the substantially planar pivoting motion of the rocker arm about the rigid housing into linear motion of the cam shifting pins 84 and 86 which are associated with the rigid housing, and in a direction substantially parallel to the axis of the housing 26 and therefore in a direction substantially perpendicular to the plane of pivoting motion of the rocker arm 40.

It has been noted that rocker arm 40 has a pivotal relationship to the housing 26, and that it is carried thereon at the upper bearing 122 on bearing post 58 and lower bearings 124 and 126 against bearing plates 128. The bearings are firmly secured to the rigid housing; and adjustment of the harness 102 about the housing 26 and against the lower end 108 of rocker arm 40 may be effected by the provision of the elongated slot 106. Further, elongated slot 130 in each of the wings 112 permits adjustment in a back and forth direction as indicated at the arrow 133 in FIG. 9 for interaction between the face 120 of each wing 112 with its opposing lobe 100 on the bell crank 90. By the inclusion of slots 106 in harness 102 and 130 in wings 112, field adjustment by qualified service personnel may easily be effected; and minor variations in dimensional tolerances of the components as they are manufactured are easily accommodated. It will be clear from the description hereafter that dwell time, or time delay, from the initiation of a roll-stop operation may be minimized by adjustment ofthe harness 102 and wings 112.

The cam plate 66 has a cam face 132 formed thereon, which cam face is comprised of the shaped periphery (or a substantial portion thereof) ofthe cam plate 66. The cam face 132, at every point therealong, is substantially perpendicular to the plane of the cam plate 66: and the cam plate 66 is symmetrical about a plane of symmetry which extends through the axis of the shaft 68, and which may be best described as an extension of the axis of index pin 72 when the cam plate 66 is in a neutral position as illustrated in FIGS. 1 or 6. In that position, an indent 134 coacts with the upper end of the index pin 72, as discussed hereafter. A pair ofindices 136 and-138 is formed in the cam plate 66, one at each side thereof, so as to preserve the symmetry thereof. It will be noted that the upper end of the index pin 72 is substantially semispherical; and conveniently the upper end of the index pin 72 comprises a hardened steel ball 140 seated in a suitable recess formed in the pin. The dimensions of the upper end of the index pin 72, and of the indices 136 and 138 formed in cam face 132 of cam plate 66, are such that when the cam plate 66 is rotated to the position illustrated in either of FIGS. 7 or 8, the upwardly urged index pin 72 will coact with either of the indices to retain the cam plate 66 in its rotated-Le, indexed-position. When the cam plate is in its indexed position, the bearing block 60 acting in groove 77 maintains the clutch 48 in driving relationship with either of the pinions 44 or 46 (as illustrated in FIGS. 2 and 3) so that driving force is delivered through crown gear 52 and shaft 54 to the driven roller 14 in the manner discussed above. It should be noted that the length of the index pin 72 may be such that it extends beyond the shoulder 82 formed in the rigid housing 26 as illustrated in FIGS. 4 and 7 so that the extended, elongated index pin 72 would then extend into one of the apertures 34 which are formed in the index plate 28. In the latter case, drive to the driven roller could only be achieved by locking or indexing the cam plate 66 into position when the entire wringer assembly including the housing 26 and rocker arm 40 is indexed onto the plate 28 by both lock means 36 and index pin 72. In any event, it is noted that the cam plate 66 may be indexed to provide drive to the rollers 12 and 14 in either direction.

The drive to the rollers 12 and 14 will continue when the cam plate 66 is indexedthe control handle 24 therefore being as indicated at 70 in either of FIGS. 2 or 3--as long as nothing happens to de-index the cam plate. In order to de index the cam plate, it is necessary to force one of the indices 136 or 138whichever is operative-away from the index pin 72. This is effected by the interaction of an outer end of the cam face 132 at one of the ends 140 or 142 of the index plate 66 with one of cam shifting pins 86 or 84. It will be recalled that the bell crank is pivoted about the pins 92 which are secured to the rigid housing 26, and that the cam shifting pins 84 and 86 are supported by a flat surface 88 which is formed in the bell crank 90. Pivoting motion of the bell crank 90 about the pin 92 in a counterclockwise direction as viewed in FIGS. 1, 2, 4 or 9 will result in an upwards motion of the cam shifting pins 84 and 86 as indicated at arrow 143 in FIG. 9. It will also be recalled that the wings 112 have faces 120 opposing lobes on the bell crank 90, and that they are associated with the rocker arm 40. Therefore, pivoting motion of the rocker arm 40 about the axis of the rigid housing 26 appears atone of the faces of one of the wings 112 as a motion thereof in the direction of arrow 133 in FIG. 9, causing the face 120 to assume the position shown in dotted lines at 120a. (Of course, only one of the faces 120 of one of the wings 112 will assume the position indicated at 120a, the other face 120 of the other wing 112 being such that it will retreat away from its respective opposed lobe 100 to the same extent as the advance of the face 120 illustrated in FIG. 9.)

In any event, it will now be noted that an advance of the face 120 against the lobe 100 causes pivoting action of the bell crank 90 about pins 92 so that the bell crank assumes a position such as that indicated in dashed lines at 90a in FIG. 9. The cam shifting pins 84 and 86, being free to move upwardly as indicated at arrow 143 upon upward motion of the surface 88 of bell crank 90, therefore assume a position such as that illustrated at 84a in FIG. 9. Both of the cam shifting pins 84 and 86 will move upwardly, and one of the cam shifting pins will strike the outer extremity of the cam face 132 at either end or 142, depending on which of indexes 136 and 138 is coacting with index pin 72. Upward motion of the upper end of the cam shifting pin against the cam face 132 will cause the cam plate 66 to begin to rotate in a direction towards its neutral position. The length and angle of the upper ends of the cam shifting pins 84 and 86 are chosen so that the relative velocity components between the ends and the outer portions 142 and 140 of the cam face 132 will force either of the indices 136 or 138 away from the upper end of index pin 72. The relative velocity components of the cam face 132 with respect to the upper end of the index pin 72 is such that, with the index pin being upwardly urged by spring 80, the index plate 66 will rotate to its neutral position because of the driving force of the index pin 72 against the cam face 132 and the relative velocity components therebetween. The upwardmost extension of the index pin 72 may be such that contact between it and the cam face 132 is broken at the neutral position. However, re-indexing of the camand co-operative relation between the index pin and one of indices 136 and l38-is obvious in view of the above discussion.

Advance of either of the faces 120 of one of the wings 112 against a lobe 100 of bell crank 90 is such that a component of the force of the pivoting motion of the wringer appears at the face 120, and is transmitted therefrom through the lobe 100 to the bell crank 90. Each lobe 100 is adapted for sliding motion along its opposing face 120 so that as the face moves from the position indicated at 120 to 120a in FIG. 9-and the bell crank to the position 90athe force is thereby transmitted from face 120 to lobe 100 through a constant moment arm measured from lobe 100 to the axis 94, being the axis of pins 92. The constant moment arm pivoting of the bell crank 90 about the axis 94 of pins 92 assures an even de-indexing operation by the action of either of cam shifting pins 84 or 86 against the outer ends 142 or 140 of cam face 132, irrespective of the direction of rotation of the driven roller 14 or the direction of the pivoting motion of the wringer 10 about the axis of the drive shaft 32. Also, symmetry is better assured, so that a pull against the wringer in either direction but of the same magnitude will cause the de-indexing operation in the same manner.

A publication of Canadian Standards Association, viz Electric Washing Machines CSA Standards C22.2, No. 53-1968, sets forth at paragraphs 4. l9.l; 4.19.2; and 4.l9.3, and paragraphs 6.7.l; 6.7.2; 6.7.3; and 6.7.4, the requirements of operation of electric washing machines which are equipped with wringers; at least so far as their roll-stop operation is concerned. An instinctive wringer according to this invention will meet those requirements and will effect roll-stop operation by de-indexing of the cam 66 to its neutral position as discussed above-upon a pull away from the interface between the rollers 12 and 14 of not greater than 20 lbs. in either direction, irrespective of the direction of drive of the driven roller 14 and at the end of the driven roller nearest the rigid housing 26. The pull may be at an angle downwards from the interface between the rollers 12 and 14 in a direction as determined by the outermost and downwardmost extensions of the drainboard 20 at the side of the wringer from which the pull is made.

A motion translating and transmitting means has been described, particularly with respect to its application to an instinctive wringer.

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

1. In an instinctive wringer, drive means including a splined shaft and a splined clutch axially shiftable thereon, said splined clutch having means to drivingly engage and disengage each one of a pair of pinions individually, said pair of pinions being both engaged with further gear means to drive at least one of a pair of rollers in said wringer; a rigid housing extending at least partially around and above and below said drive means; and operating means adapted to shift said clutch on said splined shaft, said operating means including:

a. means engageable with said clutch at the periphery thereof to shift said clutch axially along said splined shaft;

b. said clutch shifting means being pivotally connected to pivotable cam means, the pivot of said clutch shifting means being eccentric to the pivot of said pivotable cam means;

c. the cam face of said pivotable cam means being a portion of the peripheral surface thereof, and substantially perpendicular to the major plane of said pivotable cam means;

d. said pivotable cam means having a plane of symmetry taken through the pivot therefor so that said cam face is substantially symmetrical about said plane of symmetry;

e. an index pin adapted at its upper end to engage one of a pair of indexes formed in said cam face on either side of said plane of symmetry; said index pin also being adapted to maintain enga ement with said cam face during pivoting movement 0 said cam means about its pivot, and said index pin being urged upwardly at least when said cam face is engaged by the upper end thereof other than when the axis of said index pin and said plane of symmetry are co-linear;

. a rocker arm having upper and lower bearings coaxial with said splined shaft, and supporting said pair of rollers; said rocker arm being pivotable about the axis of said splined shaft independently of said rigid housing;

g. said rocker arm having a pair of wings secured thereto and projecting outwardly therefrom on opposite sides of the axis of said splined shaft;

h. said index pin extending through a generally U-shaped bell crank pivotally secured to said rigid housing on opposite sides thereof and extending around at least a portion of the periphery thereof; the axis of the pivot for said bell crank and the major plane of said pair of wings being substantially parallel;

. said bell crank having force transmitting lobes at each end thereof equally spaced from the axis of the pivot of said bell crank and adapted to cooperate with said pair of wings;

. and a further pair of pin means supported by said bell crank on opposite sides of said index pin and adapted for free upward movement upon upward movement of the supporting portion of said bell crank;

k. each of said further pair of pin means being adapted at its upper end, and being of sufficient length, to contact said cam face at a place further away from said plane of sym' metry and on the same side thereof as the index formed in said cam face which is cooperating with said index pin;

. and each of said further pin means being adapted to deindex said cam face from said index pin upon upward motion of said further pin means, so that said upwardly urged index pin then urges said cam means to pivot to the position where said plane of symmetry and the axis of said index pin are co-linear, thereby causing said clutch shifting means to disengage said clutch from the pinion with which it had been drivingly engaged.

2. The wringer of claim 1, where said index pin has a substantially semispherical upper end.

3. The wringer of claim 1, where said index pin has a ball placed at the upper end thereof so as to form a substantially semispherical upper end therefor.

4. The wringer of claim 1, where said clutch drivingly engages with either of said pair of pinions by dog means, and where there are not more than two dogs formed on each side of said clutch for driving engagement with the respective one of said pair of pinions.

5. The wringer of claim 1 further including an index plate below said rigid housing, said index plate having a plurality of spaced apertures formed therein, and means for locking said rigid housing to said index plate. 

1. In an instinctive wringer, drive means including a splined shaft and a splined clutch axially shiftable thereon, said splined clutch having means to drivingly engage and disengage each one of a pair of pinions individually, said pair of pinions being both engaged with further gear means to drive at least one of a pair of rollers in said wringer; a rigid housing extending at least partially around and above and below said drive means; and operating means adapted to shift said clutch on said splined shaft, said operating means including: a. means engageable with said clutch at the periphery thereof to shift said clutch axially along said splined shaft; b. said clutch shifting means being pivotally connected to pivotable cam means, the pivot of said clutch shifting means being eccentric to the pivot of said pivotable cam means; c. the cam face of said pivotable cam means being a portion of the peripheral surface thereof, and substantially perpendicular to the major plane of said pivotable cam means; d. said pivotable cam means having a plane of symmetry taken through the pivot therefor so that said cam face is substantially symmetrical about said plane of symmetry; e. an index pin adapted at its upper end to engage one of a pair of indexes formed in said cam face on either side of said plane of symmetry; said index pin also being adapted to maintain engagement with said cam face during pivoting movement of said cam means about its pivot, and said index pin being urged upwardly at least when said cam face is engaged by the upper end thereof other than when the axis of said index pin and said plane of symmetry are co-linear; f. a rocker arm having upper and lower bearings co-axial with said splined shaft, and supporting said pair of rollers; said rocker arm being pivotable about the axis of said splined shaft independently of said rigid housing; g. said rocker arm having a pair of wings secured thereto and projecting outwardly therefrom on opposite sides of the axis of said splined shaft; h. said index pin extending through a generally U-shaped bell crank pivotally secured to said rigId housing on opposite sides thereof and extending around at least a portion of the periphery thereof; the axis of the pivot for said bell crank and the major plane of said pair of wings being substantially parallel; i. said bell crank having force transmitting lobes at each end thereof equally spaced from the axis of the pivot of said bell crank and adapted to co-operate with said pair of wings; j. and a further pair of pin means supported by said bell crank on opposite sides of said index pin and adapted for free upward movement upon upward movement of the supporting portion of said bell crank; k. each of said further pair of pin means being adapted at its upper end, and being of sufficient length, to contact said cam face at a place further away from said plane of symmetry and on the same side thereof as the index formed in said cam face which is co-operating with said index pin; l. and each of said further pin means being adapted to de-index said cam face from said index pin upon upward motion of said further pin means, so that said upwardly urged index pin then urges said cam means to pivot to the position where said plane of symmetry and the axis of said index pin are co-linear, thereby causing said clutch shifting means to disengage said clutch from the pinion with which it had been drivingly engaged.
 2. The wringer of claim 1, where said index pin has a substantially semi-spherical upper end.
 3. The wringer of claim 1, where said index pin has a ball placed at the upper end thereof so as to form a substantially semi-spherical upper end therefor.
 4. The wringer of claim 1, where said clutch drivingly engages with either of said pair of pinions by dog means, and where there are not more than two dogs formed on each side of said clutch for driving engagement with the respective one of said pair of pinions.
 5. The wringer of claim 1 further including an index plate below said rigid housing, said index plate having a plurality of spaced apertures formed therein, and means for locking said rigid housing to said index plate. 